CONTROL SYSTEM SUITABLE FOR GLASSWARE FORMING MACHINE

Abstract: A control system for a member driven by the pneumatic piston and cylinder (15) under the control of a solenoid driven proportional pneumatic valve (16) which receives valve command signals from a servo control card (32) which includes a microprocessor and a memory, the card repetitively calculating acceleration-limited values for the command signals on the basis of an algorithm and a motion profile stored in the memory, the values used in computing the algorithm being derived from transducers (25, 26, 27) which sense the pressures of opposite sides of the piston and the position of the driven member.

Description: Title: Control System suitable for Glassware Forming Machine Field of the invention This invention relates to a control system especially a control system suitable for use in a glassware forming machine, and to an electronically controlled pneumatic valve for controlling the movement of a moveable member in such a machine. Background to the invention In a common type of glassware forming machine, the so-called I.S. machine a gob of molten glass is formed at a blank station into a parison, the parison is transferred to a blow station at which it is blown into a container, and the blown container is then removed from the machine to a cooling station and thence to a conveyor . The parison when it is transferred from the blank station to the blow station, and the blown container when it is moved from the blow station to the cooling station, are at comparatively high temperatures, and the glass of which they are formed is readily deformable. Consequently, movement of the parison and the blown container has to be very carefully controlled to avoid distortion or damage, while at the same time such movement needs to be carried out as quickly as possible to obtain the maximum output from the machine. In the case of movement of the parison from the blank station to the blow station, this is usually performed by an invert mechanism which carries the parisons of hot glass from the blank station through about 180° about a horizontal axis, to the blow station. In the case of movement of the blown container from the blow station to the cooling station, this is usually performed by a take out mechanism, which picks the blown containers up from the blow station and moves them, in a vertical orientation, through an arcuate path to the cooling station. Critical control of the movement of the take out mechanism and of the invert mechanism during their operation to move the glass is necessary, in order to avoid distortion of the still soft glass and damage due to any sudden uncontrolled motion. There are certain other mechanisms in a glassware forming machine where critical control of the movement of a mechanical member is desirable, in that faster and more precise operation and a longer life can thus be obtained. In glass machines, the motive power for the various mechanisms is normally comparatively low pressure air at about 3.2 bar. Electrical power has been used, but suffers from the disadvantage that the severe ambient conditions, i.e. the high temperatures caused by the presence of molten glass, means that electrical motors robust enough to give reliable service over a long period of time tend not only to be bulky, but also very expensive. Hydraulic power has also been used, and has some advantage, but requires significantly more maintenance than pneumatic power and suffers from the attendant high fire risk if a leak of the hydraulic oil takes place, again because of the presence of hot glass. One of the problems in using pneumatic power for driving the mechanisms is that, because of the compressibility of air and the comparatively high inertia of the mechanisms to be driven, it is difficult to obtain movement of the components reliably and accurately between desired rest positions; thus a degree of oscillation about an eventual rest position is very difficult to avoid. In International Patent Application W093/18445 is described a control system which utilizes a solenoid driven proportional pneumatic valve to control the movement of a driven member by a piston and cylinder device, the operation of the valve being controlled by an electronic signal processing system which is provided with a feed back from a simple transducer which senses the position of the driven member. This control system operates satisfactorily, but suffers from the drawback that it requires a sensitive transducer which will nevertheless resist the severe environment of a glassware making machine, and such transducers are not readily available. It is an object of the present invention to provide an alternative control system which will achieve the aforesaid critical control and which will operate reliably in the severe environment of a glassware making machine. The present invention provides in one of its aspects a control system for controlling the movement of a driven member arranged to be driven between first and second positions by a pneumatic piston and cylinder device comprising a solenoid driven proportional pneumatic valve adapted to control the supply of air under pressure to the piston and cylinder device, a transducer which senses the position of the driven member, pressure sensors which sense the pressures on opposite sides of the piston of the piston and cylinder device, and an electronic signal processing system incorporating a memory in which a motion profile is stored, which processing system throughout each cycle receives as a feedback from the transducer the position of the driven member and the pressure on opposite sides of the piston and which produces control signals for the valve in accordance with a repetitive algorithm which takes account of (a) the displacement of the driven member from the motion profile, (b) the velocity of the driven member as derived from the rate of change of its position, and (c) the force exerted on the driven member as derived from the pressure difference across the piston so that the valve supplies air to the piston and cylinder device to cause the member to move from rest at the first position to rest at the second position in a manner determined by the motion profile with the velocity and acceleration of the driven member being controlled so that the member moves from rest at the first position to rest at the second position without exceeding permitted maximum values of acceleration. A control system according to the invention as set out in the last preceding paragraph is particularly suitable for use in controlling the movement of a mechanism such as a take out mechanism or an invert mechanism in a glass forming machine, where it is desired to follow a specified motion profile. When a take out mechanism is operating, because the take out arm is moved in an arc about a horizontal axis, there is a cyclical variation of the load on the arm. Similar variations of the load can occur with other mechanisms, such as an invert mechanism. Preferably, in a control system according to the invention the algorithm also takes account of variation of the load of the member with movement of the piston and cylinder device. The present invention also provides in another of its aspects, an operating mechanism for a glassware forming machine comprising a driven member, a pneumatic piston and cylinder device arranged to operate the driven member, and a control system as hereinbefore defined in which the proportional pneumatic valve controls the supply of air under pressure to the piston and cylinder device. Description of Embodiment There now follows a description of a mechanism embodying the invention to be read with reference to the accompanying drawings in which: Figure 1 is a schematic diagram of a pneumatic servo takeout mechanism for glassware for a glassware forming machine; Figure 2 indicates schematically the construction of the control valve shown in Figure 1; Figure 3 is a block diagram of a servo control card; and associated components;and Figure 4 is a block diagram of a controller for the take out mechanism and is an illustration of the embodied algorithm. Referring first to Figure 1 , the illustrated takeout mechanism comprises a driven member in the form of a pivoted arm 10 carrying tongs 12 adapted to grip three formed glassware containers at a blow mould station. The arm 10 is drivable in rotation about its pivot axis by a rack which is an extension of a piston rod 14 carrying a piston head 15 of a pneumatic piston and cylinder device. The displacement of said device is controlled by a proportional pneumatic valve 16 (see also Figure 2) operated by a solenoid 18 fed with appropriate control signals. whereby the arm 10 is swung upwardly and over to transfer the glassware from the moulding station to a cooling station. Having set the glassware down at the cooling station, the tongs 12 are released and the arm 10 is returned under pneumatic control, ready to pick up the next three formed containers at the moulding station. For maximum throughput of glassware in the machine, the transfer of the arm 10 between stations should take place as quickly as practicable. This presents no problem on the return stroke of the arm; but during the forward stroke, when the aim is transferring formed glassware which is still soft, distortion damage or defects of the glassware can occur if the motion is not carefully controlled. The transfer motion needs to take place as rapidly as possible compatible with the avoidance of such distortion, damage and defects in the glassware, and it is a principal object of the present invention to provide a solution to this problem. The proportional pneumatic valve 16 is fed by a pneumatic air supply 20 at a nominal pressure of 45 p.s.i, and the piston has associated with it a manual bypass valve 24. The solenoid 18 which operates the valve 16 is supplied with control signals fed from processing electronics which throughout each cycle receives inputs from a position transducer 26 associated with the piston 15, (and thus with the arm 10 which is proportionally pivoted by the piston) and from two pressure sensors 25 and 27 which are respectively arranged to sense the pressure above and below the piston. Referring now to Figure 3, card 32 provides a signal processing system. This comprises a micro-controller 28 which is connected to a proportional valve controller 34 and provides spool position demand signals to the valve controller 34 through a digital/analog converter 36. The micro-controller 28 is connected through an analog/digital converter 40 to the position transducer 26 which provides signals indicating the actual position of the mechanism and to the pressure sensors 25 and 27 which provide signals indicating the pressures above and below the piston head 15. The micro controller 28 is also connected to an EPROM 42 and RAM 48 in either of which is stored the profile program for the mechanism movement. The machine comprises a supervisory computer 48 which is connected through a network interface 46 to the micro-controller 28 and then to the RAM 48 to which the algorithm information is passed and stored and which is accessed by the micro-controller 28 at appropriate times. The synchronization signal is supplied to the micro-controller 28 through a digital interface 50. Alternatively, the micro-controller 28 can provide the synchronization signal internally. A UART (universal Asynchronous Receiver Transmitter) 52 is connected to a Hand Held Terminal (HHT) 30 to allow the constant factors of the algorithm program to be adjusted to enable the actual profile to be followed to be modified. These factors are provided to the micro-controller 28. Thus the micro-controller 28 takes the profile program from the EPROM 42 or RAM 48, the algorithm program from the EPROM 42 or RAM 48, and the individual factors from the EPROM 42, RAM 48 UART 52, or Supervisory Computer 44 and combines them to enable it repetitively to use the algorithm program and profile program to enable it to provide the necessary spool position demand signals to the valve controller 34. An operator interface is provided. The embodiment uses the HHT 30 or the Supervisory Computer 44. If desired, the HHT 30 can be dispensed with and the necessary individual factors provided from the supervisory computer 44. The supervisory computer 44 comprises display means which is arranged to display motion profile data. The HHT 30 is connected to the card 32 and by its operation the motion profile data can be modified. The valve controller 34 and the valve 16 form a servo system, the controller 34 receiving a feed-back signal indicating the actual spool position from a sensor 38 and developing the actual valve control signals from the valve spool demand signals supplied by the micro-controller 28 and the feed-back sienals from the sensor 38. An algorithm, which may be used to generate an output signal to the valve controller 34 to cause the valve 16 to control movement of the piston 14 and thus of the arm 10, will now be described with reference to Figure 4, which is a functional block diagram of the machine controller. The various parts of the controller are described below. Force. Velocity. Position and Input Filters In all cases a simple low-pass filter is used to reduce high frequency signal noise. One example, given below is the low pass filter for the force signal. The filtered force, fforce, is given by fforce = af*fz-l + bf*FORCE (1) where: af and bf are constants in the force filter fz-1 is the calculated filtered force from the previous algorithm iteration FORCE is force value calculated during the present iteration of the algorithm af = iter * T_F/(1.0 + iter*T_F) bf= 1.0/(1.0 + iter*T_F) iter is the iteration rate of the controller (Hz) T_F is the filter constant which is tuned to give an acceptable level of valve noise The filters are all of the same form. The equations for the force filter are shown above. The corresponding variables used in the other filters are listed in the table below; the filtered vasriable being calculated by an equation of the same form as equation (1). The input, force position and velocity signals are filtered in a similar manner. The values of the filter constants for the input, force, velocity and position are tuned upwards from a very low value until an acceptable level of noise is achieved on each signal whilst still achieving the required performance. The penalty for increasing the value too high is loss of performance due to the increased time delay which accompanies the increased smoothing effect of the filter. The input filter prevents noise from being transmitted through the system. The filter helps to prevent high frequency resonances within the controlled system from being excited. The corresponding variables for the four filters are listed below : Force Velocity Input Position fforce FVELOC infil FPOS {filtered variable] T_F τ_v T_I T_P [Tuned filter constants] af av ai ap )calculated filter bf bv bi bp )constants FORCE veloc demand POSIT Values during present iteration fz-1 fvz-1 infil-1 fpz-1 Filtered values from previous iteration veloc the calculated mechanism velocity demand this comes from the demand profile. A value from this profile is used by the algorithm at each iteration POSIT this is the position of the mechanism. A new value for POSIT is obtained from the position sensor at each iteration of the algorithm Error Limiter This is used to clip the value of the error so that it remains within pre-chosen limits. This can be useful, for example, to prevent overshoot of the mechanism in cases where the mechanism has been prevented from following the profile because it becomes jammed with another mechanism and is then suddenly released. error = infil - FPOS error is clipped to be within a selected range - - ERRLIM Non-Linearity and K-P End point stiffness is improved by multiplying the forward gain factor K-P by a further factor "nlerr". When the error becomes zero the function "nlerr" rises to its maximum value. The rate at which "nlerr" rises, and the range over which it rises can be altered by tuning the parameter "SHARPN" in the equation shown below. The value of "NLOFF" is tuned to give a suitable value to the peak of "nlerr". nlerr = 1.0 + NL_OFF/(l .0 + SHARPN*error*error) The error is then multiplied by the forward gain. The variable uv is defined by the equation uv = K_P*nlerr*error uv may be described as the active error reducing component of the algorithm. Differentiation The position value is used to calculate the velocity as shown : veloc = w2*(POSIT - pz-l)*ITER + 2.0*zx*vz-l - x2*vz-2 w2= VFILT*VFILT zx = 1.0 - VFILT x2 = zx*zx vz-1 is the value of the velocity from the last iteration (unfiltered) vz-2 is the value of the velocity from the last but one iteration (unfiltered) pz-1 is the value of the position from the last iteration (unfiltered) The equation for evaluating veloc is a digital filter, which provides as estimate of velocity based on the position measurement at discrete times. VFILT is the tuned filter constant. It is used to obtain an acceptable compromise between noise and time delay. With rising VFILT, time delay is reducing, though noise in the velocity estimate due to noise on the position signal is increasing. As VFILT is reduced, noise is reduced at the expense of increased time delay, which may introduce oscillation into the mechanism movement. A compromise hase to be made. uf is defined by uf = uv - [FVELOC*K_D] where K_D is the velocity gain. uf is the input to a force control loop. If the mechanism is in the correct demand position and the velocity is zero, the force required to move the mechanism to the correct position is zero and the value of uf is also zero. Force Model Gravity exerts force on the moving parts of the mechanism. In the take out this force is not constant. The weight of the piston and rod, and of the arm and tong head contribute to this force. As the mechanism moves from the blow mold through the vertical position and then down to the deadplate, the effect of the weight of the arm and tong head varies. It falls to a minimum at the 90 degree position. The force exerted by the pressures above and below the piston is calculated. The effective force available to move the mechanism is "FORCE": gravity = Gl*9.81 - G2*9.81*COS(10.0 - POSIT)*0.3142) FORCE = (PRESS _B*A_below- PRESS_A* A_above) - gravity gravity this is the name of the gravity term. G 1 mass of piston rod and piston G2 related to mass of arm and tong head and to effective distance of centre of gravity. Value found by experimentation. PRESS_A pressure above piston PRESS_B pressure below piston A_above effective area of top of piston A_below effective area below piston The values "PRESS_A" and "PRESS_B" come from the pressure transducers. Values are read at each algorithm iteration. Calculation of valve demand output The valve demand u is calculated from u = uf- (fforce*K_F) where: K_F is the force gain. The valve demand "u" is clipped to the physical limits of the system. Update History After the valve actuation signal is sent, the variables used within the filters and the differentiator are updated, e.g. : fz-1 - = fforce vz-2- = vz-1 vz-1- = veloc The algorithm then repeats.

Claims: Claims A control system for controlling the movement of a driven member arranged to be driven between first and second positions by a pneumatic piston and cylinder device comprising:- a solenoid driven proportional pneumatic valve adapted to control the supply of air under pressure to the piston and cylinder device, a transducer which senses the position of the driven member, pressure sensors which sense the pressure on opposite sides of the piston of the piston and cylinder device, an electronic signal processing system incorporating a memory in which a motion profile is stored, which processing system throughout each cycle receives as a feed-back from the transducer the position of the driven member and the pressure on opposite sides of the piston and which produces control signals for the valve in accordance with a repetitive algorithm which takes account of (a) the displacement of the driven member from the motion profile, (b) the velocity of the driven member as derived from the rate of change of its position, and, (c) the force exerted on the driven member as derived from the pressure difference across the piston, so that the valve supplies air to the piston and cylinder device to cause the member to move from rest at the first position to the second position in a manner determined by the motion profile, with the velocity and acceleration of the driven member being controlled so that the member moves from rest at the first position to rest at the second position without exceeding permitted maximum values of acceleration. 2 A control system according to claim 2 wherein the algorithm also takes account of variation of the load on the member with movement of the piston and cylinder device 3 A control system according to one of claims 1 and 2 wherein the repetitive algorithm is as set out hereinbefore and defined. 4. A system according to any one of claims 1 to 3 wherein operation of the pneumatic valve is controlled by a valve controller connected to the valve by two lines, one of which supplies a dπve signal to the valve to drive the spool of the valve and the other of which returns a spool position indication signal. 5. A system according to any one of claims 1 to 4, wherein the pressure sensing transducers sense the pressures in the cylinder above and below the piston and the position-sensing transducer causes movement of the piston. 6. A system according to claim 5, wherein the three transducers supply signals through analogue/digital converters to a servo control card incorporating a micro-controller which instructs the valve controller through a digital/analogue converter. 7. A system according to claim 6, wherein the micro-controller is connected to a memory which stores a profile program for the movement of the driven member. 8. A system according to claim 7, wherein a supervisory computer for the machine is connected through an interface of the servo control card to pass algorithm information to the memory, which information is accessed by the valve controller under the control of a s\ nchronisation signal 9 A system according to claim 8, wherein means are provided to enable the constant factors of the algoπthm information to be analysed and adjustments stored in the memory 10 A s\ stem according to claim 9. wherein the micro-controller repeti eh accesses the memory tor the profile program, force limits, algorithm program and am factor adiustments and combines the accessed information to generate position demand signals fed to the valve controller. 1 1. A system according to any one of claims 1 to 10, wherein the algorithm operates repetitively to generate position signals subject to a valve demand limit, as the basis of a filtered force valve, a filtered velocity value, and a filtered position error demand value subject to an error limit. 12. A system according to claim 1, wherein the algorithm operates on the basis of the functional block diagram of Figure 4 hereinbefore described. 13. An operating mechanism for a glassware forming machine comprising a driven member, a pneumatic piston and cylinder device arranged to operate the driven member, and a control system according to any one of the preceding claims in which the proportional pneumatic valve controls the supply of air under pressure to the piston and cylinder device. 14. An operating mechanism according to claim 13, in which the driven member is part of a takeout mechanism. 15. An operating mechanism according to claim 14, in which the driven member is part of an invert mechanism. 16. A control system for a driven member substantially as hereinbefore described with reference to the accompanying drawings.

Inventors: COUNSELL JOHN, PLATER NEIL JAMES, ROSKILLY ANTHONY PAUL, COUNSELL, JOHN, PLATER, NEIL, JAMES, ROSKILLY, ANTHONY, PAUL
Applicants: COUNSELL JOHN, EMHART GLASS MACH INVEST, PLATER NEIL JAMES, ROSKILLY ANTHONY PAUL, COUNSELL, JOHN, EMHART GLASS MACHINERY INVESTMENTS INC., PLATER, NEIL, JAMES, ROSKILLY, ANTHONY, PAUL
Application year: 1994
Main classification: C03B9
IPC codes: C03B9, G05B19, G05D16